JP2001280104A - Electric power plant - Google Patents

Abstract

PROBLEM TO BE SOLVED: To improve power generating efficiency, by operating a mixed medium turbine so that an exhaust temperature of the mixed medium turbine is not more than a sea water temperature or an atmospheric temperature and by heating mixed medium liquid by low temperature exhaust heat such as sea water, atmosphere, or the like. SOLUTION: An electric power plant is provided with: a heating apparatus 8 heating mixed medium including low boiling point medium; a gas-liquid separator 10 separating the mixed medium into high concentration mixed medium steam and low concentration mixed medium steam; the mixed medium turbine 11 driven by the separated high concentration mixed medium steam; a vapor condenser device 14 cooling and returning mixed fluid of the mixed medium turbine exhaust and the low concentration mixed medium; a heat exchanger 18 heat-exchanging the returned mixed medium with the sea water or the atmosphere; a condenser 21 condensing at least part of the high concentration mixed medium steam separated in the gas-liquid separator 10; and a supercooling device 13 supercooling cooling fluid by using coolant formed by adiabatic expansion of the condensed medium. The supercooled fluid supercooled by the supercooling device 13 is supplied to the liquid returning device 14 as cooling medium.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

The present invention relates to a power plant, and more particularly to a power plant using a mixed medium containing a low-boiling medium as a medium for driving a turbine.

[0002]

2. Description of the Related Art With economic development in recent years, power demand has been supported by personal consumption such as enlargement of home appliances and spread of air conditioning, and both industrial and consumer use have been steadily increasing.
Of these power demands, many are converted to cold heat and used for cooling.

At present, as a power generation method having high thermal efficiency, a gas turbine is driven by high-temperature and high-pressure combustion gas obtained by burning natural gas, and steam is generated by high-temperature gas discharged from the gas turbine. Is known, and its thermal efficiency is 40 to 50%.

On the other hand, there is also known a cogeneration technique in which turbine bleeding is performed, steam or hot water is produced in a heat exchanger, transported to a long distance by a pipeline to supply heat, and simultaneously generate power. The overall thermal efficiency is 60 to 80% when this cogeneration is adopted.

[0005] In Japan, cooling demand is higher in heat utilization than in Europe and the United States. Therefore, a method using an absorption refrigerator that obtains cold heat using hot water or steam as a heating source is advantageous in terms of thermal efficiency. Further, in a light water type nuclear power plant with low thermal efficiency only by power generation, for example, when a 1.1% kW class boiling water type nuclear power plant performs 30% bleeding and uses heat, the power generation output is 776 MWe and the heat output is 1245 MWt. The heat efficiency can be reduced to about 61.4%, and the heat use efficiency can be greatly improved compared to 33.5% when only power generation is performed.

On the other hand, a steam turbine driven by steam generated by a heat source, a condenser for condensing exhaust gas from the steam turbine, means for returning condensate generated by the condenser to a heat source, steam Heat exchange means for exchanging heat between the exhaust gas from the turbine and the mixed medium, separation means for separating the mixed medium heated by the heat exchange means into liquid and gas, and gaseous mixing separated by the separation means A mixed-medium turbine driven by a medium, mixing means for mixing an exhaust gas from the mixed medium and a liquid mixed medium separated by the separating means, condensing means for condensing the mixed mixed medium, and condensing means There has been proposed a power plant with high thermal efficiency, in which a water / ammonia mixed medium cycle having a means for returning the condensate generated in the above step to the heat exchange means is combined (Japanese Patent Laid-Open No. 9-2097).
No. 16).

[0007]

In a mixed medium cycle using a mixed medium containing a low-boiling-point medium as a working medium as described above, the exhaust temperature of the mixed-medium turbine is reduced because the working medium has a high vapor pressure even at a low temperature. By lowering it, the turbine output can be increased.

In view of the above, the present invention can sufficiently lower the exhaust temperature of the mixed-medium turbine, further improve the power generation efficiency, and reduce the exhaust temperature of the mixed-medium turbine below the seawater temperature or the atmospheric temperature. It is an object of the present invention to obtain a power plant that can easily improve its power generation efficiency when operated.

[0009]

The invention according to claim 1 is
A gas-liquid separator that separates a mixed medium containing a low-boiling medium heated by a heating device into a high-concentration mixed-medium vapor and a low-concentration mixed-medium liquid, and the high-concentration mixed-medium vapor separated by the gas-liquid separator A driven mixed-medium turbine, a condensate for cooling and condensing a mixed fluid of the mixed-medium turbine exhaust and the low-concentration mixed medium, and a mixed medium condensed by the condensate is heated with seawater or the atmosphere. A heat exchanger to be exchanged, and a reflux device that refluxes the mixed medium that has passed through the heat exchanger to the heating device,
At least a part of the high-concentration mixed medium vapor separated by the gas-liquid separator is supplied, and the condenser of the refrigerant generation system that condenses the high-concentration mixed medium vapor and the medium condensed by the condenser are insulated. A supercooler that cools the cooling fluid with a refrigerant obtained by expanding the supercooler, and the supercooled fluid cooled by the supercooler is supplied to the condenser as a cooling medium. And

According to a second aspect of the present invention, there is provided a mixed-medium turbine driven by a mixed medium containing a low-boiling medium heated by a heating device, a condensate for cooling and condensing the mixed-medium turbine exhaust, A gas-liquid separator that is supplied after a part of the mixed medium condensed in the condenser is heated by the mixed medium turbine exhaust and separates into a high-concentration mixed-medium vapor and a low-concentration mixed-medium liquid; A heat exchanger for heat-exchanging a mixture of the remaining mixed medium and the high-concentration mixed medium vapor separated by the gas-liquid separator with seawater or the atmosphere,
A reflux device that refluxes the mixed medium that has passed through the heat exchanger to the heating device, a condenser of a refrigerant generation system that condenses the mixed medium heated by the heating device, and adiabatic expansion of the medium condensed by the condenser. And a supercooler for cooling the cooling fluid with the refrigerant obtained by supplying the supercooled fluid cooled by the supercooler to the condenser as a cooling medium. And mixing the low-concentration mixed medium separated by the above and the mixed medium turbine exhaust upstream of the condenser.

According to a third aspect of the present invention, in the first or second aspect of the present invention, there is provided a subcooling release tank for separating a supercooled fluid in a supercooled state by a subcooler into ice and water,
An ice storage tank for storing the ice separated in the supercooling release tank, wherein the ice in the ice storage tank is guided to the first heat exchange section of the condenser in the form of ice slurry, and the supercooling is released. The cooling water separated in the tank is introduced into the second heat exchange section of the condenser.

According to a fourth aspect of the present invention, in the invention according to the third aspect, a part of the cooling medium introduced into the first heat exchange section of the condenser is removed from the middle of the first heat exchange section. It is characterized in that it is returned to the ice storage tank and used for thawing ice, and the cooling medium flowing out of the first heat exchange section is introduced into the freshwater storage tank.

According to a fifth aspect of the present invention, in the first or third or fourth aspect of the present invention, the gas-liquid separator is provided by mixing the mixed medium heated by the heating device with a high-concentration mixed medium vapor and a low-concentration mixed medium. A first gas-liquid separator for separating into a liquid, and a second gas for further separating the low-concentration mixed-medium liquid separated from the low-concentration mixed-medium liquid separated by the first gas-liquid separator. The high-concentration mixed medium vapor separated by the second gas-liquid separator is supplied to an intermediate stage of a mixed-medium turbine, and the low-concentration mixed medium liquid is introduced into a condenser. It is characterized by the following.

According to a sixth aspect of the present invention, in the first or third or fourth aspect of the present invention, the gas-liquid separator is provided by mixing the mixed medium heated by the heating device with the high-concentration mixed medium vapor and the low-concentration mixed medium vapor. A first gas-liquid separator for separating into a mixed medium liquid, and a second gas-liquid separator for further separating the low-concentration mixed medium liquid separated by the first gas-liquid separator into a high-concentration mixed medium vapor and a low-concentration mixed medium liquid Wherein the high-concentration mixed medium vapor separated by the second gas-liquid separator is supplied to the condenser of the refrigerant generation system.

The invention according to claim 7 is the invention according to claim 1 or 3.
In the invention according to any one of the first to fifth aspects, a second mixed medium turbine is provided between the heating device and the gas-liquid separator, and the mixed medium heated by the heating device is supplied to the second mixed medium turbine. This is driven, and the exhaust gas of the second mixed medium turbine is introduced into the gas-liquid separator.

According to an eighth aspect of the present invention, in the invention according to the seventh aspect, the mixed medium heated by the heating device is branched at an inlet side of the second mixed medium turbine, and the second mixed medium turbine and the refrigerant are mixed. It is characterized in that it is introduced into each condenser of the production system.

According to a ninth aspect of the present invention, in the second aspect, a part of the high-concentration mixed medium vapor separated by the gas-liquid separator is replaced with the refrigerant instead of the mixed medium heated by the heating device. It is characterized in that it is supplied to the condenser of the production system.

The invention according to claim 10 is the invention according to claims 1 to 9
In the invention according to any one of the above, a heat exchanger for heat exchange between the mixed medium and seawater condensed by the condensate, and a cold seawater storage tank for storing seawater cooled by the heat exchanger. ,
The cold seawater stored in the cold seawater storage tank is supplied to a condenser and a supercooler of the refrigerant generation system.

The invention according to claim 11 is the invention according to claims 1 to 1
In the invention according to any one of the first to third aspects, the condenser is provided with a third heat exchange unit for cooling seawater.

The invention according to claim 12 is based on claim 4.
In the invention according to the first aspect, the cooling medium flowing out of the first heat exchange section of the condenser is introduced into the freshwater storage tank and stored, and the freshwater stored in the freshwater storage tank is guided to the subcooler to be supercooled. It is characterized by doing.

According to a thirteenth aspect of the present invention, in the first or the second aspect of the present invention, a supercooling release tank for releasing the supercooled state of the supercooled fluid which has been supercooled by the supercooler, and the supercooled tank thereof An ice storage tank for storing the ice generated in the release tank; guiding the ice in the ice storage tank to the heat exchange section of the condenser in the form of ice slurry, where the thawed water that has exchanged heat is transferred to the ice The method is characterized in that the ice is returned to the storage tank, and the defrosted water in the ice storage tank is guided to a subcooler by a circulation pump to be supercooled.

According to a fourteenth aspect of the present invention, in the first or second aspect of the present invention, the surface seawater is introduced into the heat exchanger for cooling the mixed medium condensed by the condenser, and the condenser and the condenser are cooled. The cooler is characterized by supplying deep cold seawater.

According to a fifteenth aspect of the present invention, in the invention according to the fourteenth aspect, at least a part of the mixed medium condensed in the condensate is exchanged with the atmosphere, or the condensate is further condensed. After cooling in, it is introduced into a heat exchanger.

The invention according to claim 16 is the invention according to claims 1 to 1
5. In the invention according to any one of the aspects 5, a part of the mixed medium condensed by the condensate is guided to a heat exchange unit of a condenser of the refrigerant generation system, heat-exchanged, and then introduced into the heating device. It is characterized by.

[0025] The invention according to claim 17 is the invention according to claims 1 to 1
In the invention according to any one of the first to sixth aspects, the low-concentration mixed medium liquid separated by the gas-liquid separator and the high-concentration mixed medium that has passed through the supercooler of the refrigerant generation system are used as the driving fluid, An ejector for sucking turbine exhaust is provided.

The invention according to claim 18 is a gas-liquid separator for separating a mixed medium containing a low-boiling medium heated by a heating device into a high-concentration mixed-medium vapor and a low-concentration mixed-medium liquid;
A mixed-medium turbine driven by the high-concentration mixed medium separated by the gas-liquid separator, a condensate for cooling and condensing a mixed fluid of the mixed-medium turbine exhaust and the low-concentration mixed medium, and the condensate A heat exchanger for selectively exchanging heat with the atmosphere of the mixed medium condensed in step (a), and a heating device for heating the mixed medium condensed.

The invention according to claim 19 is the invention according to claims 1 to 1
In the invention according to any one of Items 8, the heating device is a thermal power plant or a nuclear power plant.

[0028] The invention according to claim 20 is based on claim 1.
In any one of the inventions according to any one of Items 1 to 19,
It is a mixed medium of water and ammonia.

[0029]

Embodiments of the present invention will be described below with reference to the accompanying drawings.

FIG. 1 is a diagram showing a first embodiment of the present invention. The power generation system of the present invention comprises a nuclear power generation system 1, a mixed medium system 2, a refrigerant generation system 3, and an ice production system 4. It is configured. In FIG. 1, reference numeral 5 denotes a nuclear reactor of the nuclear power generation system 1,
The steam generated in the nuclear reactor 5 is introduced into a steam turbine 6 where it performs work and drives a generator 7 connected to the steam turbine 6 to generate power.

On the other hand, exhaust steam that has performed work in the steam turbine 6 is condensed in a condenser 8, and the condensed water is pressurized by a feed water pump 9 and returned to the nuclear reactor 5.

A mixed medium containing a low-boiling medium such as a mixed medium of ammonia and water is introduced into the heat exchange section 8a of the condenser 8 of the reactor power generation system 1, where it is heated by the exhaust steam from the steam turbine 6. You. The mixed medium heated by the condenser 8 is sent to the gas-liquid separator 10 of the mixed medium system 2, where the high-concentration mixed medium vapor having a high concentration of the low-boiling component and the low-concentration mixed medium having a low concentration of the low-boiling component are low. It is separated into a medium liquid. The high-concentration mixed-medium vapor separated by the gas-liquid separator 10 is sent to the mixed-medium turbine 11, performs expansion work, operates the mixed-medium turbine 11, and drives the generator 12. On the other hand, the exhaust of the mixed medium that has performed work in the mixed medium turbine 11 is provided to the subcooler 1 of the ice production system 4 described later.
The high concentration mixed medium from 3 is merged and introduced into the condenser 14.

The low-concentration mixed medium liquid separated by the gas-liquid separator 10 is cooled by a first heat exchanger 15 for preheating the mixed medium supplied to the condenser 8 and then cooled by a first throttle. Valve 16
Adiabatic expansion at the upstream side of the condenser 14 and mixing with the exhaust gas of the mixing medium turbine 11 at the upstream side of the condenser 14.
1 and the high concentration mixed medium from the supercooler 13 are mixed and absorbed by the adiabatic expanded low concentration mixed medium.

The mixed medium introduced into the condenser 14 is cooled and condensed there, and the condensed liquid is pressurized by the pressurizing pump 17.
After heat exchange with seawater in the second heat exchanger 18 and heating,
It is returned to the condenser 8 via the first heat exchanger 15 as a cooling medium.

On the other hand, a branch conduit 20 is branched from a steam supply conduit 19 for guiding the high-concentration mixed medium vapor separated by the gas-liquid separator 10 to the mixed medium turbine 11, and the branch conduit 20 is used to convert seawater into a cooling medium. Connected to the condenser 21 of the refrigerant generation system 3. Thus, the branch conduit 2
The high-concentration mixed medium vapor branched to zero is cooled and condensed in the condenser 21 by heat exchange with seawater. Condenser 21
The mixed medium condensed in the above is adiabatically expanded by the expansion valve 22, introduced into the heat exchange section 13a of the supercooler 13 of the ice production system 4, performs heat exchange, and is pressurized by the pressure pump 23,
After passing through the third heat exchanger 24 using seawater as a cooling medium and adiabatically expanding at the second throttle valve 25, it is combined with the exhaust gas from the mixed medium turbine 11.

The subcooler 13 is supplied with seawater cooled by a fourth heat exchanger 26 described later.
The seawater is supercooled by heat exchange with the mixed medium adiabatically expanded by the supercooler 13. The supercooled seawater is then introduced into a subcooling release tank 27, where it is separated into concentrated seawater and ice, and the ice is stored in an ice storage tank 28 and the ice storage tank 2
8 is thawed into an ice slurry state, guided by the first transport pump 29 to the first heat exchange section 14 a of the condenser 14 as a cooling medium, and mixed with the mixed medium introduced into the condenser 14. Heat exchange is performed and cooling is performed. First heat exchange section 14a
A part of the cooling medium is returned to the ice storage tank 28 and used for thawing the ice. The cooling medium that has passed through the first heat exchange unit 14a is introduced into the freshwater storage tank 30. On the other hand, the concentrated seawater separated in the subcooling release tank 27 is introduced into the second heat exchange section 14b of the condenser 14 by the second transport pump 31, where the mixed medium is cooled and then the fourth heat exchanger The water is sent to a seawater discharge pipe 32 where heat exchange is performed with seawater.

When the power demand in the daytime is large, the high-concentration mixed medium vapor is not branched into the refrigerant generation system 3 through the branch pipe 20 but is entirely introduced into the mixed medium turbine 11, and the mixed medium turbine 11 is discharged. 11 is operated and power is generated by the generator 12. The exhaust gas that has performed work in the mixed medium turbine 11 is supplied to the gas-liquid separator 10.
Is mixed with the low-concentration mixed medium that has passed through the first heat exchanger 15 and the first throttle valve 16 and is introduced into the condenser 14.

The ice stored in the ice storage tank 28 is thawed into an ice slurry to be supplied to the first heat exchange section 14 a of the condenser 14 by the first transport pump 29.
Therefore, the mixed medium introduced into the condenser 14 exchanges heat with the defrosting water flowing in the first heat exchange section 14a of the condenser 14 and is completely restored. Then, the condensed liquid is pressurized by the pressurizing pump 17, heat-exchanges with seawater in the second heat exchanger 18, is heated to near the seawater temperature, and is further mixed with the low-concentration mixed medium in the first heat exchanger 15. The heat is exchanged and returned to the condenser 8.

On the other hand, when nighttime power demand is small, at least a part of the high-concentration mixed medium vapor separated by the gas-liquid separator 10 is branched to the branch pipe 20 and introduced into the condenser 21 of the refrigerant generation system 3. Is done. The mixed medium introduced into the condenser 21 is cooled and condensed there in a heat exchange section through which seawater flows. The condensed mixed medium is adiabatically expanded by the expansion valve 22 to become a refrigerant, guided to the heat exchange section 13a of the subcooler 13 of the ice production system 4, and exchanges heat with the seawater cooled by the fourth heat exchanger 26. And the seawater is supercooled. The mixed medium in which the seawater is supercooled by the supercooler 13 is pressurized by the pressurizing pump 23, cooled by the third heat exchanger 24 by the seawater, and then adiabatically expanded by the second throttle valve 25, and is mixed. The exhaust gas from the turbine 11 is combined with the exhaust gas,
It is mixed and absorbed by the low concentration mixed medium separated at zero.

The seawater supercooled by the supercooler 13 is guided to a subcooling release tank 27 where it is separated into concentrated seawater and ice, and the ice is stored in an ice storage tank 28. On the other hand, the concentrated seawater is supplied to the second condenser pump 14 by the second transport pump 31.
And the cooling medium is cooled. Then, the seawater that has passed through the second heat exchange section 14b is discharged to the seawater discharge pipe 32 after being heated in the fourth heat exchanger 26.

As described above, in the first embodiment of the present invention, the mixed medium is heated by the condenser of the nuclear power generation system, and the high-concentration mixed medium vapor and the low-concentration mixed medium liquid are separated by the gas-liquid separator. In the daytime, the mixed medium vapor drives the mixed medium turbine with all separated medium vapor to generate electricity, and when the exhaust gas is condensed to produce a condensate, the ice produced and stored at night is thawed. By cooling with the cryogenic water thus obtained, the back pressure of the turbine is sufficiently reduced, and the turbine output can be increased to cope with the peak power demand during the day. In addition, the low-temperature condensate cooled with defrost water is pressurized by a pressurizing pump, then heat-exchanged with seawater to heat it to near seawater temperature, and heated by the condenser of the nuclear power generation system to mix. The amount of high-concentration mixed medium vapor for driving the medium turbine can be increased, the power generation amount can be increased, and the power generation efficiency is further improved in conjunction with the increase in turbine output by lowering the mixed medium turbine exhaust temperature. Can be done.

In the above embodiment, the mixed medium is heated by the exhaust of the steam turbine operated by the saturated steam generated in the nuclear reactor. However, instead of the nuclear reactor, general heating is performed. Steam generated by the boiler may be used, and superheated steam may be used instead of saturated steam. Also,
Combustion gas or the like can also be used as a heat source of the superheater. In the above-described embodiment, the high-concentration mixed-medium vapor is selectively introduced into the mixed-medium turbine and the condenser. However, the mixture may be appropriately distributed and introduced into both to produce ice. .

FIG. 2 is a view showing a second embodiment of the present invention. The mixed medium heated by the condenser 8 is introduced into the first gas-liquid separator 33, where it is mixed with a high-concentration mixed medium. Separated into vapor and low concentration mixed medium liquid. The high-concentration mixed medium vapor separated by the first gas-liquid separator 33 is supplied to the mixed medium turbine 11 or the condenser 21 of the refrigerant generation system 3.
Selectively supplied to

This point is the same as that shown in FIG.
A second gas-liquid separator 35 is connected to the first gas-liquid separator 33 via a pressure reducing valve 34. The low-concentration mixed medium separated by the first gas-liquid separator 33 is supplied to the pressure reducing valve 3.
After being decompressed by 4, it is introduced into a second gas-liquid separator 35, where it is separated into a high concentration mixed medium vapor and a low concentration mixed medium liquid. The high-concentration mixed medium vapor separated by the second gas-liquid separator 35 is supplied to the intermediate stage of the mixed medium turbine 11 as a working medium. On the other hand, the low-concentration mixed medium liquid separated by the second gas-liquid separator 35 is mixed with the exhaust gas of the mixed medium turbine 11 through the first heat exchanger 15 and the first throttle valve 16, and is returned together with the exhaust gas. The liquid is introduced into the vessel 14 and returned. Other points are the same as the embodiment shown in FIG.

Thus, also in this embodiment, when the power demand in the daytime is large, the entire amount of the high-concentration mixed medium is guided to the mixed medium turbine 11, so that sufficient power can be obtained, and the power demand in the nighttime is small. At times, the high-concentration mixed medium separated by the first gas-liquid separator 33 is introduced into the condenser 21 of the refrigerant generation system 3, ice is made in the same manner as described above, and ice is stored in the ice storage tank 28, Be prepared when needed. In addition, since the high-concentration mixed-medium vapor separated by the first gas-liquid separator 33 and the second gas-liquid separator 35 is introduced into the mixed-medium turbine 11, the amount of high-concentration mixed-medium vapor can be further increased. Output can be improved.

FIG. 3 is a diagram showing a third embodiment of the present invention. As shown in FIG. 2, the gas-liquid separator is composed of a first gas-liquid separator 33 and a second gas-liquid separator 35. The high-concentration mixed medium vapor separated by the first gas-liquid separator 33 is always introduced into the mixed medium turbine 11. on the other hand,
The low-concentration mixed medium liquid separated by the first gas-liquid separator 33 is decompressed by the pressure reducing valve 34 and then the second gas-liquid separator 35
Will be introduced. In the second gas-liquid separator 35, the mixed medium is further separated into a high-concentration mixed-medium vapor and a low-concentration mixed-medium liquid, and the separated high-concentration mixed medium vapor is entirely introduced into the condenser 21 of the refrigerant generation system 3. Is done. The low-concentration mixed-medium liquid is mixed with the exhaust gas of the mixed-medium turbine 11 via the first heat exchanger 15 and the first throttle valve 16, and is introduced into the condenser 14 together with the exhaust gas to be condensed. Other points are the same as the embodiment shown in FIG.

In this embodiment, however, FIG.
The same operation and effect as those described above can be obtained.

FIG. 4 is a view showing a fourth embodiment of the present invention, in which a mixed medium turbine 11 is provided between a condenser 8 and a gas-liquid separator 10 on the same axis. Two mixed media turbines 36 are provided. Then, the mixed medium heated in the condenser 8 is supplied to the second mixed medium turbine 36, and the mixed medium exhausted there is introduced into the gas-liquid separator 10. Other points are the same as those shown in FIG.

Therefore, in this embodiment, similarly to the first embodiment, a high turbine output can be obtained in the mixed-medium turbine in the daytime, and ice is produced and stored at nighttime, and the mixture is stored in the daytime. For cooling the mixed medium.

FIG. 5 is a diagram showing a fifth embodiment of the present invention, which is a modification of the embodiment shown in FIG. In FIG. 5, the mixed medium heated by the condenser 8 is selectively supplied to the second mixed medium turbine 36 and the condenser 21 and separated by the gas-liquid separator 10. The high-concentration mixed medium vapor is supplied to the mixed medium turbine 11. Other points are the same as those shown in FIG.

That is, in the daytime when power demand is high, the mixed medium heated by the condenser 8 is introduced into the second mixed medium turbine 36, where it performs work, and is coaxial with the second mixed medium turbine 36. The generator 12 is driven together with the connected mixed medium turbine 11. On the other hand, the mixed medium that has performed work in the second mixed medium turbine 36 is introduced into the gas-liquid separator 10, where it is separated into a high-concentration mixed-medium vapor and a low-concentration mixed-medium liquid. Then, the separated high-concentration mixed-medium vapor is introduced into the mixed-medium turbine 11, where work is performed. Further, the low-concentration mixed medium liquid passes through the first heat exchanger 15 and the first throttle valve 16 and is supplied to the mixed medium turbine 11.
And is introduced into the condenser 14 together with the exhaust gas to be condensed.

In this embodiment, however, FIG.
The same effects as those of the embodiment shown in FIG.

FIG. 6 is a view showing a sixth embodiment of the present invention. The mixed medium heated by the condenser 8 is introduced into the mixed medium turbine 11 or the condenser 21 of the refrigerant generation system 3. . The mixed medium that has performed the work in the mixed medium turbine 11 is introduced into the condenser 14 and is returned. The mixed medium condensed in the condenser 14 is pressurized by the pressurizing pump 17, heat-exchanged with seawater in the second heat exchanger 18 and heated, and then further heated in the fifth heat exchanger 37. Heated by seawater,
It is returned to the condenser 8 via the pressure pump 38.

On the downstream side of the second heat exchanger 18, a part of the mixed medium condensed by the condenser 14 is branched, and a sixth heat exchanger into which the exhaust gas of the mixed medium turbine 11 is introduced. 3
After being led to 9 and heated, it is introduced into the gas-liquid separator 40. In the gas-liquid separator 40, the mixed medium heated in the sixth heat exchanger 39 is separated into a high-concentration mixed medium vapor and a low-concentration mixed medium liquid, and the high-concentration mixed medium vapor is separated from the fifth heat exchanger. At the inlet side of 37, the concentration of the mixed medium mixed into the mixed medium and flowing to the condenser 8 side is increased. On the other hand, the low-concentration mixed medium liquid separated by the gas-liquid separator 40 is supplied to the first throttle valve 1.
6, the mixture is mixed with the exhaust gas of the mixed medium turbine 11 and introduced into the condenser 14. Other points are the same as those of the first embodiment.

In this embodiment, however, the first
The same effect as that of the embodiment can be obtained.

FIG. 7 is a diagram showing a seventh embodiment of the present invention, and shows a modification of FIG. That is, in this embodiment, at least a part of the high-concentration mixed medium vapor separated by the gas-liquid separator 40 is selectively supplied to the condenser 21, and the remaining high-concentration mixed medium vapor is condensed. Table 8
And mixed with the mixing medium directed to. The mixed medium heated by the condenser is introduced only to the mixed medium turbine 11. The other points are the same as those shown in FIG. 6, and have the same effects.

FIG. 8 is a view showing an eighth embodiment of the present invention, in which a condenser 21, a third heat exchanger 24, and a subcooler 1 are shown.
3. A seawater supply pipe 41 that supplies seawater to each heat exchange section of the fourth heat exchanger 26 and the second heat exchanger 18 has a cold seawater storage tank 42 downstream of the second heat exchanger 18. The cold seawater stored in the cold seawater storage tank 42 is supplied by the water supply pump 43 to the third heat exchanger 24 and the subcooler 1.
3 and so on. The other points are the same as the first embodiment.

In the daytime when power demand is high, seawater is supplied to the heat exchange section of the second heat exchanger 18 in the mixed medium system 2 to exchange heat with the mixed medium from the condenser 14, and the heat The seawater cooled by the exchange is stored in the cold seawater storage tank 42. When ice is manufactured at night, the cold seawater stored in the cold seawater storage tank 42 is supplied to the supercooler 13 of the ice manufacturing system 4 and used for manufacturing ice.
The condenser 21 and the third heat exchanger 24 of the refrigerant generation system 3
And is used for cooling the high concentration mixed medium vapor.

Therefore, not only the same effects as in the first embodiment are obtained, but also the cold heat obtained by heating the mixed medium led out of the liquid condensing unit 14 is stored in the cold seawater storage tank 42, By using this at the time of ice production, the amount of refrigerant required for ice production can be reduced, and the required power can be reduced.

FIG. 9 is a view showing a ninth embodiment of the present invention, in which a third heat exchange section 14c through which seawater is circulated is provided in the condenser 14. Other points are the same as those of the plant shown in FIG.

During nighttime when power demand is low, seawater is also introduced into the third heat exchange section 14c of the condenser 14 and the introduction of seawater into the second heat exchanger 18 is stopped. The mixed medium turbine 11 introduced into the condenser 14
Can be more effectively condensed, and the function of the condenser 14 can be ensured even when the amount of ice produced at night varies.

FIG. 10 is a view showing a tenth embodiment of the present invention, in which ice is produced from seawater, stored, thawed in the daytime and used for cooling the condenser of the mixed medium system. After that, it stopped being used as fresh water, and was configured as a circulating ice cooling system.

That is, the subcooler 1 of the ice production system 4
In 3, fresh water stored in the fresh water storage tank 30 is set to reflux. In the daytime when power demand is high, the ice stored in the ice storage tank 28 is thawed into the first heat exchange section 14a of the condenser 14 of the mixed medium system 2 and the slurry is conveyed. The heat is exchanged with the exhaust gas of the mixed-medium turbine 11 by the pump 29, and part of the heat is exchanged with the exhaust gas of the mixed-medium turbine 11. . Then, at night, the fresh water stored in the fresh water storage tank 30 is introduced into the supercooler 13 to be in a supercooled state, and the supercooled state is released in the supercool release tank 27 to produce ice. Further, a third heat exchange section 14c for circulating seawater is provided in the condenser 14, and the third heat exchange section 14c also cools the exhaust gas of the mixed medium turbine 11. Other points are the same as those shown in FIG.

Thus, in this embodiment, the thawed water used for cooling the condenser 14 is recovered and used for producing ice, so that the amount of refrigerant required for producing ice can be reduced.

FIG. 11 is a view showing an eleventh embodiment of the present invention. In the tenth embodiment, a fresh water storage tank is omitted and fresh water in an ice storage tank 28 is circulated. The water is supplied to the subcooler 13 by a pump 41.

At night, the fresh water portion of the ice stored in the ice storage tank 28 is introduced into the supercooler 13 by the circulation pump 41, where it is supercooled, and is supercooled in the supercool release tank 27. The condition is released and ice is generated, and the ice is stored in the ice storage tank 28. Other points are the same as those shown in FIG. Therefore, FIG.
The same effect as that shown in FIG.

FIG. 12 is a view showing a twelfth embodiment of the present invention, which has a configuration similar to that shown in FIG. 9, and the second heat exchanger 18 of the mixed medium system 2 includes a surface seawater. Is supplied, the third heat exchanger 14c of the condenser 14, the condenser 21 in the refrigerant generation system 3, and the third heat exchanger 2
4. The fourth in the subcooler 13, and the ice making system 4.
Is supplied with deep seawater.

By supplying deep seawater to the subcooler 13 when producing ice at night, the energy required for producing ice can be reduced.
By supplying deep cold seawater to the third heat exchange unit 14c, the output of the mixed medium turbine can be increased.

FIG. 13 is a view showing a thirteenth embodiment of the present invention, which has substantially the same structure as that shown in FIG. 12, and is pressurized by the pressurizing pump 17 of the mixed medium system 2. After a part of the mixed medium is branched and guided to the cooling dower 44, the heat is exchanged with the second heat exchanger 18 or the fourth heat exchange section 14 d of the condenser 14, and then the second heat exchanger 18 is cooled. To be introduced.

In the summer, however, the mixed medium pressurized by the pressurizing pump 17 in the mixed medium system 2 is branched and led to the cooling tower 44, where it is heated by the atmosphere and the solar heat to be heated by the second heat exchanger 18 Will be introduced. on the other hand,
In winter, the mixed medium pressurized by the pressurizing pump 17 is branched, guided to the cooling tower 44, cooled by the atmosphere, and then introduced into the fourth heat exchange section 14d of the condenser 14 to perform heat exchange. After performing, it is introduced into the second heat exchanger 18. As described above, by using the atmosphere at the time of high temperature in summer and at the time of low temperature in winter, the thermal efficiency can be improved as hotter and colder.

FIG. 14 is a view showing a fourteenth embodiment of the present invention, which has a configuration substantially similar to that shown in FIG. A part of the mixed medium is branched and supplied to the heat exchange unit 21a of the condenser 21 in the refrigerant generation system 3, where the mixed medium heated and exchanged heat is mixed with the mixed medium at the inlet side of the condenser 8 in addition to the mixed medium. It is made to join the department.

Thus, when ice making is performed at night,
Since the mixed medium pressurized by the pressurizing pump 17 is guided to the condenser 21 and exchanges heat with the high-concentration mixed medium vapor to perform heat recovery, the effect of producing cold heat is improved.

FIG. 15 is a view showing a fifteenth embodiment of the present invention. Compared with the one shown in FIG. 1, the first throttle valve 16 and the second throttle valve 25 are omitted. Condenser 1
4 is provided with an ejector 45 for sucking the exhaust gas of the mixed medium turbine 11. That is, in the condenser 14,
A drive nozzle 46 is provided for supplying the low-concentration mixed medium liquid cooled by the first heat exchanger 15 and the high-concentration mixed medium pressurized by the pressurizing pump 23 in the refrigerant generation system 3. When the low-concentration mixed-medium liquid and the high-concentration mixed medium are ejected from the nozzle 46, exhaust gas from the mixed-medium turbine 11 is sucked into the condenser 14.

By using the high pressure of the low-concentration mixed medium liquid separated by the gas-liquid separator 10 as driving energy for the ejector 45 and sucking the exhaust gas from the mixed medium turbine 11, the mixed medium turbine 11 The back pressure can be sufficiently reduced, the turbine output can be increased, and the temperature of the chilled water for condensing exhaust gas can be increased, so that the required amount of stored ice can be reduced.

FIG. 16 is a view showing a seventeenth embodiment of the present invention, in which the refrigerant generation system 3 and the ice production system 4 are omitted from those shown in the first embodiment and the like. Then, a part of the mixed medium pressurized by the pressurizing pump 17 is branched and guided to the cooling tower 47, and thereafter, the heat is transferred to the second heat exchanger 18 or the fourth heat exchanging part 14 d of the condenser 14. After the replacement, the heat is introduced into the second heat exchanger 18.

In the summer, however, the mixed medium pressurized by the pressurizing pump 17 in the mixed medium system 2 is branched and led to the heat exchange section of the cooling tower 47, where the mixed medium is heated by the atmosphere and sunlight, and then the second mixture is heated. To the heat exchanger 18. On the other hand, in winter, the mixed medium pressurized by the pressurizing pump 17 is branched, guided to the cooling tower 47 and cooled by the atmosphere, and then introduced into the fourth heat exchange section 14d of the condenser 14 where heat exchange is performed. , And then introduced into the second heat exchanger 18. Therefore, in this embodiment, the atmospheric temperature in summer and winter can be effectively used, and the thermal efficiency can be improved.

That is, since the working medium of the mixed medium cycle has a high vapor pressure even at a low temperature, the exhaust gas temperature of the mixed medium turbine can be lowered. Therefore, when the mixed medium turbine exhaust temperature is operated at the seawater temperature or the atmospheric temperature or lower, the power generation efficiency can be improved by heating the mixed medium at the seawater or the atmospheric temperature as shown in FIG.

[0078]

As described above, the present invention provides a mixed-medium system having a mixed-medium turbine operating on a mixed medium containing a low-boiling medium, and the exhaust of the mixed-medium turbine is generated by the mixed medium. Since the cooling medium cooled by the refrigerant is returned to the condenser by leading it to the condenser, the turbine exhaust temperature can be sufficiently reduced to increase the turbine output, and the thermal efficiency can be greatly improved. . In addition, when the mixed medium turbine exhaust temperature is operated at the seawater temperature or the atmospheric temperature or lower, the power generation efficiency can be further improved by heating the mixed medium condensate with seawater, the atmosphere, or other low-temperature exhaust heat.

[Brief description of the drawings]

FIG. 1 is a diagram showing a schematic configuration of a first embodiment of the present invention.

FIG. 2 is a diagram showing a schematic configuration of a second embodiment of the present invention.

FIG. 3 is a diagram showing a schematic configuration of a third embodiment of the present invention.

FIG. 4 is a diagram showing a schematic configuration of a fourth embodiment of the present invention.

FIG. 5 is a diagram showing a schematic configuration of a fifth embodiment of the present invention.

FIG. 6 is a diagram showing a schematic configuration of a sixth embodiment of the present invention.

FIG. 7 is a diagram showing a schematic configuration of a seventh embodiment of the present invention.

FIG. 8 is a diagram showing a schematic configuration of an eighth embodiment of the present invention.

FIG. 9 is a diagram showing a schematic configuration of a ninth embodiment of the present invention.

FIG. 10 is a diagram showing a schematic configuration of a tenth embodiment of the present invention.

FIG. 11 is a diagram showing a schematic configuration of an eleventh embodiment of the present invention.

FIG. 12 is a diagram showing a schematic configuration of a twelfth embodiment of the present invention.

FIG. 13 is a diagram showing a schematic configuration of a thirteenth embodiment of the present invention.

FIG. 14 is a diagram showing a schematic configuration of a fourteenth embodiment of the present invention.

FIG. 15 is a diagram showing a schematic configuration of a fifteenth embodiment of the present invention.

FIG. 16 is a diagram showing a schematic configuration of a sixteenth embodiment of the present invention.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 1 Nuclear power generation system 2 Mixing medium system 3 Refrigerant generation system 4 Ice production system 5 Nuclear reactor 6 Steam turbine 8 Condenser 10 Gas-liquid separator 11 Mixing medium turbine 13 Subcooler 14 Condenser 15 First heat exchange Device 16 First throttle valve 17, 23 Pressure pump 18 Second heat exchanger 20 Branch conduit 21 Condenser 22 Expansion valve 24 Third heat exchanger 26 Fourth heat exchanger 27 Supercooling release tank 28 Ice storage Tank 29 First transport pump 30 Freshwater storage tank 33 First gas-liquid separator 34 Pressure reducing valve 35 Second gas-liquid separator 36 Second mixed medium turbine 37 Fifth heat exchanger 38 Pressurizing pump 39 Sixth Heat exchanger 40 gas-liquid separator 42 cold seawater storage tank 43 feedwater pump 44,45 cooling tower

 ──────────────────────────────────────────────────続 き Continuing on the front page (72) Inventor Shunji Kawano 2-4, Suehirocho, Tsurumi-ku, Yokohama-shi, Kanagawa Prefecture Inside the Toshiba Keihin Plant (72) Inventor Takayuki Marume 1-chome Shibaura, Minato-ku, Tokyo No. 1-1 Toshiba Corporation Head Office (72) Inventor Tomoko Ogata 1-1-1, Shibaura, Minato-ku, Tokyo F-term (Reference) 3G081 BA02 BA20 BB07 BC00 BD02 BD04 BD10 DA16

Claims (20)

[Claims] 1. A gas-liquid separator for separating a mixed medium containing a low-boiling medium heated by a heating device into a high-concentration mixed-medium vapor and a low-concentration mixed-medium liquid, and a high-liquid separator separated by the gas-liquid separator. A mixed-medium turbine driven by the concentrated mixed-medium vapor, a condenser for cooling and condensing a mixed fluid of the mixed-medium turbine exhaust and the low-concentration mixed medium, and a mixed medium condensed by the condensate in seawater. Or a heat exchanger for exchanging heat with the atmosphere, a recirculation device for recirculating the mixed medium passing through the heat exchanger to the heating device, and at least a part of the high-concentration mixed medium vapor separated by the gas-liquid separator. Is supplied, and a condenser of a refrigerant generation system that condenses the high-concentration mixed medium vapor, and a supercooler that cools a cooling fluid with a refrigerant obtained by adiabatically expanding the medium condensed by the condenser. Have that supercool The supercooled fluid cooled by the vessel, characterized in that so as to supply a cooling medium to the medium condenser, power plant. 2. A mixed-medium turbine driven by a mixed medium containing a low-boiling medium heated by a heating device, a condenser for cooling and returning the mixed-medium turbine exhaust, and a condensate in the condenser A gas-liquid separator that is supplied after a part of the mixed medium is heated by the mixed-medium turbine exhaust and separates into a high-concentration mixed-medium vapor and a low-concentration mixed-medium liquid; A heat exchanger for exchanging a mixture of the remainder of the medium and the high-concentration mixed medium vapor separated by the gas-liquid separator with seawater or the atmosphere, and refluxing the mixed medium passed through the heat exchanger to the heating device A refluxing device, a condenser of a refrigerant generation system that condenses the mixed medium heated by the heating device, and a condenser that cools a cooling fluid by a refrigerant obtained by adiabatically expanding the medium condensed by the condenser. With cooler The supercooled fluid cooled in the subcooler is supplied as a cooling medium in the medium condenser,
A power plant, wherein the low-concentration mixed medium separated by the gas-liquid separator and the mixed medium turbine exhaust are mixed on an upstream side of a condenser. 3. A subcooling release tank for separating a supercooled fluid supercooled by a subcooler into ice and water, and an ice storage tank for storing the ice separated in the subcooling release tank. Guiding the ice in the ice storage tank to the first heat exchange section of the condenser in the form of ice slurry, and cooling the water separated in the subcooling release tank to the second heat exchange section of the condenser. The power plant according to claim 1, wherein the power plant is introduced into the power plant. 4. A part of the cooling medium introduced into the first heat exchange section of the condenser is returned to the ice storage tank in the middle of the first heat exchange section and used for thawing ice. 4. The power plant according to claim 3, wherein the cooling medium flowing out of the heat exchange unit is introduced into a freshwater storage tank. 5. A first gas-liquid separator for separating a mixed medium heated by a heating device into a high-concentration mixed-medium vapor and a low-concentration mixed-medium liquid, and a first gas-liquid separator. A second gas-liquid separator for further separating the low-concentration mixed-medium liquid separated into the high-concentration mixed-medium vapor and the low-concentration mixed-medium liquid, and separating the high-concentration mixed-medium liquid separated by the second gas-liquid separator. 5. The power plant according to claim 1, wherein the concentrated mixed medium vapor is supplied to an intermediate stage of the mixed medium turbine, and the low concentrated mixed medium liquid is introduced into the condenser. 6. A first gas-liquid separator for separating a mixed medium heated by a heating device into a high-concentration mixed-medium vapor and a low-concentration mixed-medium liquid, and a first gas-liquid separator. And a second gas-liquid separator for separating the low-concentration mixed-medium liquid separated into the high-concentration mixed-medium vapor and the low-concentration mixed-medium liquid, and the high-concentration mixed medium separated by the second gas-liquid separator. The power plant according to claim 1, wherein the mixed medium vapor is supplied to a condenser of the refrigerant generation system. 7. A second mixed medium turbine is provided between the heating device and the gas-liquid separator, and the mixed medium heated by the heating device is supplied to and driven by the second mixed medium turbine.
The power plant according to any one of claims 1 to 3, wherein the exhaust gas of the second mixed medium turbine is introduced into a gas-liquid separator. 8. A mixed medium heated by a heating device is branched at an inlet side of a second mixed medium turbine, and introduced into the second mixed medium turbine and a condenser of a refrigerant generation system, respectively. The power plant according to claim 7, characterized in that: 9. A high-concentration mixed medium vapor separated by a gas-liquid separator instead of the mixed medium heated by the heating device is supplied to a condenser of the refrigerant generation system. The power plant according to claim 2. 10. A heat exchanger for exchanging heat between seawater and a mixed medium condensed by a condenser, and a cold seawater storage tank for storing seawater cooled by the heat exchanger. The power plant according to any one of claims 1 to 9, wherein the cold seawater stored in the seawater storage tank is supplied to a condenser and a subcooler of the refrigerant generation system. 11. The condenser according to claim 1, further comprising a third heat exchanger for cooling seawater.
A power plant according to any one of the above. 12. The cooling medium flowing out of the first heat exchange section of the condenser is introduced into a fresh water storage tank for storage, and the fresh water stored in the fresh water storage tank is guided to a subcooler to be supercooled. The power plant according to claim 4, wherein the power generation is performed. 13. A subcooling release tank for releasing a supercooled state of a supercooled fluid supercooled by a supercooler, and an ice storage tank for storing ice generated in the supercooled release tank. Then, the ice in the ice storage tank is guided to the heat exchange section of the condenser in the form of ice slurry, where the defrosted water that has undergone heat exchange is returned to the ice storage tank, and the defrosted water in the ice storage tank is supplied to the circulation pump. The power generation system according to claim 1 or 2, wherein the system is guided to a subcooler for subcooling. 14. A heat exchanger for cooling the mixed medium condensed in the condenser, surface seawater is introduced into the heat exchanger, and deep seawater is supplied to the condenser and the supercooler. The power generation system according to claim 1 or 2, wherein 15. The method according to claim 15, wherein at least a part of the mixed medium condensed in the condenser is exchanged with the atmosphere, or cooled in the condenser, and then introduced into the heat exchanger. The power generation system according to claim 14, which performs the power generation. 16. The method according to claim 16, wherein a part of the mixed medium condensed in the condenser is guided to a heat exchange section of a condenser of the refrigerant generation system, heat-exchanged, and then introduced into a heating device. ,
The power plant according to any one of claims 1 to 15. 17. The condenser includes a low-concentration mixed medium liquid separated by a gas-liquid separator and a high-concentration mixed medium that has passed through a supercooler of a refrigerant generation system as a driving fluid, and sucks a mixed medium turbine exhaust gas. The power plant according to any one of claims 1 to 16, wherein an ejector is provided. 18. A gas-liquid separator for separating a mixed medium containing a low-boiling medium heated by a heating device into a high-concentration mixed-medium vapor and a low-concentration mixed-medium liquid; and a high-liquid separator separated by the gas-liquid separator. A mixed media turbine driven by a concentration mixed media;
A condenser for cooling and condensing a mixed fluid of the mixed medium turbine exhaust and the low-concentration mixed medium, a heat exchanger for selectively exchanging heat with the atmosphere of the mixed medium condensed by the condensate, A heating device for heating the condensed mixed medium. 19. The heating device according to claim 1, wherein the heating device is a thermal power plant or a nuclear power plant.
9. The power plant according to any one of 8 above. 20. The power plant according to claim 1, wherein the mixed medium is a mixed medium of water and ammonia.